WO2019115452A1 - Système à ressorts de rappel pour un frein à disque, ainsi que garniture de frein équipée d'un ressort de jeu - Google Patents

Système à ressorts de rappel pour un frein à disque, ainsi que garniture de frein équipée d'un ressort de jeu Download PDF

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Publication number
WO2019115452A1
WO2019115452A1 PCT/EP2018/084160 EP2018084160W WO2019115452A1 WO 2019115452 A1 WO2019115452 A1 WO 2019115452A1 EP 2018084160 W EP2018084160 W EP 2018084160W WO 2019115452 A1 WO2019115452 A1 WO 2019115452A1
Authority
WO
WIPO (PCT)
Prior art keywords
brake
spring
brake pad
caliper
lüftspielfeder
Prior art date
Application number
PCT/EP2018/084160
Other languages
German (de)
English (en)
Inventor
Werner Denhard
Jan Carach
Dietrich Golz
Juan David Hernandez
Mathias Haag
Thorsten LAHR
Original Assignee
Continental Teves Ag & Co. Ohg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Continental Teves Ag & Co. Ohg filed Critical Continental Teves Ag & Co. Ohg
Publication of WO2019115452A1 publication Critical patent/WO2019115452A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/02—Braking members; Mounting thereof
    • F16D65/04—Bands, shoes or pads; Pivots or supporting members therefor
    • F16D65/092—Bands, shoes or pads; Pivots or supporting members therefor for axially-engaging brakes, e.g. disc brakes
    • F16D65/095—Pivots or supporting members therefor
    • F16D65/097—Resilient means interposed between pads and supporting members or other brake parts
    • F16D65/0973—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces
    • F16D65/0979—Resilient means interposed between pads and supporting members or other brake parts not subjected to brake forces acting on the rear side of the pad or an element affixed thereto, e.g. spring clips securing the pad to the brake piston or caliper
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0016—Brake calipers
    • F16D2055/0029—Retraction devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2127/00—Auxiliary mechanisms
    • F16D2127/02—Release mechanisms

Definitions

  • a brake pad in this connection is a slidably arranged in the brake function module to understand which in addition to the actual friction lining and a friction lining plate or - Wegplatte depending on the design and other components and attachments such as Dämp fungsbleche, rivets, sliding plates, Verschleissan Attachen, sensors and May contain the same.
  • a fixed caliper brake caliper In a fixed caliper brake caliper is firmly connected to aggyachskomponente and has at least two on both sides of the brake disc arranged counter-acting brake piston. As a result, each brake pad is actuated by at least one brake piston acting directly on it. The brake pads slide on the brake caliper fixed sliding surfaces or components and the order catching forces from the brake pads are introduced into the caliper.
  • a fist or floating caliper brake caliper is axially displaceable or floating relative to a fixedly connected to aggyachskomponente brake holder stored.
  • One or more co-acting brake pistons are in
  • Brake caliper is arranged only on one side of the brake disc, so that the one or more brake pistons act only on one of the two brake pads directly, whereas the other brake pad is acted upon by a brake piston opposite flank of the caliper.
  • the two brake pads slide on brake holder fixed trained sliding surfaces or components and the peripheral forces from the brake pads are introduced into the brake holder.
  • the vehicle disc brakes are in principle designed so that in the dissolved state, ie before or after a Bremsbe actuation between friction ring and friction lining a so-called clearance is set.
  • This clearance describes in practice an axial distance between the oppositely arranged friction surfaces of friction lining and friction ring.
  • the gearver set the brake pad after a braking operation by low imbalances of the brake disc, which "beats back" the brake pads after the brake piston is retracted after brake pressure reduction by rubber elastic recovery of a brake piston seal
  • Such a method is simple, but associated with undesirable noise development and increased brake wear Corrosion, wear and contamination of brake pad guide sections can also significantly increase the frictional resistance of the brake pads along the actuation path negatively affect the clearance setting.
  • An object of the present invention is thus to provide an improved return spring system for adjusting the clearance with basic suitability for fixed and floating caliper brakes, which at a simplified handling and improved corrosion protection of the Lvid playing spring in all operating and wear conditions permanently reliable as uniform as possible Return torque of the brake pad guaranteed.
  • the object is achieved by a restoring spring system having features according to claim 1.
  • the invention provides that the L9596feder explicitly assigned to a single brake pad and forms out as a tension spring. Further, the L9596feder between the brake pad and a brake caliper is elastically tensioned and permanently ver at least one point of force application to the brake pad ver, preferably permanently connected.
  • the force application point is provided on a side facing away from the friction lining of the friction lining carrier plate.
  • the air spring is thus a part of the
  • the loss secured connection to the brake pad can in this case in particular by However, riveting also clinching or otherwise, preferably carried out by forming technology.
  • the Lsymmetrically devis is completely arranged on a side facing away from the friction lining side of the friction lining carrier plate.
  • a space-neutral solution Darge offered brake lining guide sections are exempted from the additional feathering, any negative effects in terms of the brake actuation feeling and brake pedal behavior are avoided.
  • the invention further provides that the Lsymmetricspielfeder in the manner of a self-contained spring clip has a spring body and an end connected to the spring body and bent from this spring tab, wherein the spring body and the spring tab at its connection point opposite end each have an interface for a force-transmitting Attachment to another component.
  • the Fe derlaschensche interface can preferably be designed for simplified penetration of a rivet as a fastening eye.
  • the spring body can have two sections in the circumferential direction spaced apart support arms and the spring clip between the two support arms, with which it is connected end.
  • Such designed Lsellfeder can be punched particularly quickly and inexpensively in a single operation of sheet material.
  • the highly integrated design becomes one high functionality achieved on a comparably small surface with a reduced use of materials.
  • the spring tab in an unloaded initial state before mounting on the brake pad relative to the spring body in a brake pad opposite axial direction.
  • a biasing force is built up and the spring body is elastically pressed rattle-free in abutment function to the brake pad.
  • a simplified, easy and fast and tool-less feasible preloading and fixing the air spring on the caliper can be alized according to a preferred embodiment re by the interface-side end of the spring body bent and with a radially directed
  • Breakthrough is provided for locking on a caliper formed on the radially directed projection.
  • a bevel for simplified sliding during Verrastungsvorgang.
  • the interface-side end of the spring body having an axially directed opening which is aligned with a corresponding Ge robuse monieri in the caliper designed as an abutment.
  • a screw for releasably fixing the L predominantlyspielfeder on the abutment is also conceivable as an alternative.
  • the engaging engagement detent attack particularly advantageous, one piece without a geson derter locking element with spring-integrated locking elements are rea l cry.
  • the interface-side end of the spring body can be bent for insertion through an axially aligned in the caliper housing breakthrough and provided with at least one integrated and radially resilient and integrally inte grated axially acting locking element.
  • Force application point of the air spring preferably be provided in a central position on the Reibbelagaplatte in particular in the region of the Reib perennialhetas.
  • FIG.l spatial view of a brake pad with an air spring mounted thereon according to a preferred Ausry tion of the invention
  • FIG. 2 shows a spatial representation of an embodiment of the invention from the restoring spring system on the example of a fixed caliper brake.
  • FIG. 3 shows a preferred embodiment of the Lsymmetricspielfeder spatially and in side view.
  • FIG 4 shows a side view of a brake lining with a clearance spring mounted thereon in an unassembled initial state (a) and at operational deflection (b)
  • FIGS. 7 and 8 show various embodiments of two subgroups of a second interface type.
  • FIG. 9 Various embodiments (a, b) of a third interface type.
  • the return mounting system 1 comprises a brake lining 2 with an air-play spring 7 explicitly assigned thereto and attached thereto.
  • the brake lining 2 comprises a friction lining carrier plate 4, which is provided with a friction lining 3 on one side.
  • the Lsymmetricspielfeder 7 is arranged in the axial direction A completely on a side facing away from the friction lining 3 side of the friction lining carrier plate 4 and formed as a tension spring.
  • the Lsymmetricspielfeder has two interfaces 11,12.
  • the first interface 11 is used for attachment to the brake pad 2 and at the same time forms the force application point 8.
  • the second interface 12 is used to tension and tie the Lvid play spring 7 on the brake caliper 6 to pull the brake pad 2 axially in its return direction.
  • the Lsymmetrically inextricably by forming a rivet to the brake pad 2 during its manufacture, so that it is handled together with the brake pad 2 in all subsequent process steps.
  • theumpstellbefederungssystem 1 is arranged and clamped in an analogous manner in the caliper.
  • FIG 3 is a preferred embodiment of the Lvid playing spring 7 in an unloaded initial state as it is present before attachment to the brake pad 2, shown.
  • the Lvid play spring 7 is integrally formed as a plate spring and has a spring body 9 stretched in the radial direction, which forms in its first end portion a pair of circumferentially spaced support arms 13. In the circumferential direction U arranged between the support arms 13 and end connected to this is a spring tab 10th
  • the spring tab 10 designed in this embodiment as a fastening eye, provided for attachment to the brake pad interface 11.
  • another interface 12 which for the force-transmitting connection is provided to the brake caliper 6.
  • the spring clip 10 is in relation to the spring body 9 axially in a direction opposite to the brake lining 2 direction (the return direction) plastically bent so that their end
  • Interface 11 to the spring body 9 axially has a defined biasing deflection Sv.
  • FIG. 4 The view a) of Figure 4 shows a brake pad 2 with an attached Lsymmetricspielfeder 7 in a non-operational initial state, such as when transporting or immediately after the inserts of the brake pad 2 in the brake caliper 6, but before the tensioning of the air spring 7 is present ,
  • the spring tab 10 is resiliently biased to the friction lining carrier plate 4, is also on this and is connected at its interface 11 with the brake pad 2.
  • a force application point 8 is formed at the junction, whereby the spring-body-side interface 12 is acted upon by a biasing force Fv axially toward the brake pad 2 or against the return direction and the spring body 9 pressed against the friction lining carrier plate 4 rests flat.
  • the view b) of Figure 4 shows a staggered during braking in the direction of actuation brake pad 2 with the L predominantly play spring 7 in the corresponding braking position.
  • the spring body-side interface 12 is in engagement with a brake-resistant projection 15.
  • the Fe derlasche 10 is pushed through the opening in the spring body 9 between the support arms 13, whereby the Lsymmetricspielfeder 7 is scissor-like tension to form an increased operating force Fb.
  • the operating force Fb acts on the brake pad 2 as a tensile force directed in the return direction.
  • Fig. 5 5 shows, by way of example, three force application points 8 designed differently on a brake pad 2, each with suitably modified air play springs 7.
  • Lsymmetrically adapted to the variations As an example, here is a brake pad 2 shown in FIG 2, which is for simultaneous application by two brake piston 21,21 'is provided and this two spaced in order circumferential direction spaced, with separate sheets underlined piston contact surfaces 22,22'.
  • the friction surface of the brake pads 2 is substantially mirror-symmetrical in the circumferential direction, the central axis M extends approximately through the radial Reib perennialachigoddling of the respective brake pad. 2
  • the force application point 8 of the Lsymmetrically should ideally be arranged in Reibfestech. This is often not exactly feasible for reasons of space, so that the position of the force application point 8 should be provided in as central as possible and the Reib lakehistosky approached position.
  • the force is attack point 8 in the circumferential direction symmetrically between the piston contact surfaces 22,22 ', in the radial direction, however, at a distance to the center axis M.
  • the L bulkspielfeder 7 is correspondingly shortened in its radial extension a) or extended b), c).
  • FIGS. 6 to 9 show by way of example and not exclusively different forms of interfaces between the Lsymmetricspielfeder 7 and the brake caliper 6 and illustrated by the following.
  • connection of the Lsymmetricallyfeder 7 to the brake caliper 6 is in the embodiment shown by a snap relation ship as latching the interface 12 on a brake caliper 6 in the radial direction pre-stretched formed before jump 15.
  • the interface-side end of the spring body 9 in the brake pad 2 opposite axial direction la is like a rule bent and provided with a radially directed breakthrough 14.
  • the interface-side end of the spring body 9 is pressed with a finger or tool axially supported to the caliper out until the interface 12 passes over the projection and then snaps or locked.
  • An end on the spring body 9 angled shaped sliding ramp 16 facilitates sliding on the projection 15 (see Figure 6a).
  • the projection is provided on the brake pad side with a chamfer 23 for further reduction of the resistance during latching.
  • On the opposite side of the projection 15 is mechanically machined for an exact support and ver improved support in the load case.
  • Late and ⁇ are fixed by means of a separate locking element 18 on the brake caliper 6.
  • the locking element 18 is formed in the embodiment shown as a Sp Grande.
  • the interface-side end of the spring body 9 has for this purpose an axially directed opening 17, which breakthrough 19 in the mounting position with a corresponding housing 19 in the caliper 6.
  • the locking element 18 is simply inserted through both aligned openings 17,19 until it latches at the end of the housing opening 19 to form an axially acting undercut.
  • the interface-side end of the spring body 9 in the embodiment of Figure 7a is designed cranked. In the embodiment according to FIG. 7b, it is simply straight.
  • the embodiment of the Lsymmetricallytul 7 according to Fig.7c is particularly safe, for example, designed for high load cases or Vib rationscludes and this additionally with Widerha bridges 24,24 'equipped, which engage behind a corresponding sprue or other suitable shape on the brake caliper 6.
  • FIG. 8 acts in principle analogous to the embodiments of Figure 7 with the difference that instead of a cylindrical Sp Dahlpins a specially shaped expansion clamp serves as a locking element 18.
  • the expansion clamp has transversely to the push-through protruding stop elements 25, which serve to rest on the Lsymmetricspielfeder 7 and transversely to the push-through direction elastically resilient locking elements 20,20 ', which rebend after insertion through the housing opening 19 and form an axial undercut.
  • the cut center-side end of the spring body 9 is for insertion through a brake housing 6 in the axially aligned housing 19 in the brake lining 2 opposite axial direction bent and with a (Fig.9a) or more (Fig.9b) integrated, transversely to the push-through resiliently formed locking element 20 provided.
  • Their mode of action corresponds to the spreading clamp described above.
  • FIG. 10 illustrates, in conjunction with the associated force-displacement diagram according to FIG. 11, different characteristic load states of the L-displacement diagram according to FIG. 11, different characteristic load states of the L-displacement diagram according to FIG. 11, different characteristic load states of the L-displacement diagram according to FIG. 11, different characteristic load states of the L-displacement diagram according to FIG. 11, different characteristic load states of the L-displacement diagram according to FIG. 11, different characteristic load states of the Lsymmetric 8. The operating points shown in FIG. 10 are marked accordingly in FIG.
  • the spring body 9 When mounting the Lsymmetricspielfeder 7 or attachment of the spring clip 10 with its interface 11 on the brake pad 2, the spring body 9 forms an abutment, compared to the spring tab 10 while reducing the Vorspannausschung Sv and simultaneous construction of a biasing force Fv elastically pressed to the brake pad 2 and with this is riveted to form the Kraftan grip point 8 (Fig.10b).

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Abstract

L'invention concerne un système à ressorts de rappel (1) amélioré servant à régler de manière active un jeu pour un frein à disque (5) de véhicule automobile, lequel est adapté en principe à des freins à étrier fixes ou flottants et qui garantit durablement, lors d'une manipulation et d'une protection anti-corrosion améliorées, dans tous les états de fonctionnement et d'usure, un couple de rappel aussi homogène que possible de la garniture de frein (2). L'invention prévoit à cet effet que le ressort de jeu (7) est associé explicitement à la garniture de frein (2) et est réalisé sous la forme d'un ressort de traction, lequel est mis sous tension élastiquement entre la garniture de frein (2) et un étrier de frein (6) et est relié en permanence de manière imperdable, en particulier de manière inamovible, à la garniture de frein (2) sur au moins un point d'attaque de force (8). Le point d'attaque de force (8) est disposé sur un côté, opposé à la garniture de friction (3), de la plaque de support (4) de garniture de friction.
PCT/EP2018/084160 2017-12-12 2018-12-10 Système à ressorts de rappel pour un frein à disque, ainsi que garniture de frein équipée d'un ressort de jeu WO2019115452A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017222520.3 2017-12-12
DE102017222520 2017-12-12

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WO2019115452A1 true WO2019115452A1 (fr) 2019-06-20

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PCT/EP2018/084160 WO2019115452A1 (fr) 2017-12-12 2018-12-10 Système à ressorts de rappel pour un frein à disque, ainsi que garniture de frein équipée d'un ressort de jeu

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WO (1) WO2019115452A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113915260B (zh) * 2021-09-30 2023-07-28 浙江万安科技股份有限公司 一种制动器
EP4163512A1 (fr) * 2021-10-06 2023-04-12 MAT Commercial Vehicle Products GmbH Plaquette de frein
DE102022211364A1 (de) 2022-10-26 2024-05-02 Hl Mando Corporation Bremsklotz mit ohren mit mindestens einer durchgangsaussparung

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996008663A1 (fr) * 1994-09-13 1996-03-21 Kelsey Hayes Company Mecanisme de retrait de machoire pour ensemble frein a disque
JP2000220670A (ja) * 1999-01-29 2000-08-08 Tokico Ltd ディスクブレーキ
US20020043436A1 (en) * 2000-10-18 2002-04-18 Jochen Burgdorf Spot-type disc brake with a spring assembly for a brake lining
US20120085597A1 (en) * 2010-10-08 2012-04-12 Akebono Corporation (North America) Caliper assembly for disc brake system
FR3033012A1 (fr) * 2015-02-25 2016-08-26 Foundation Brakes France "frein a disque comportant au moins un ressort de rappel elastique d'un patin de freinage, ressort de rappel elastique, kit de remplacement et procede de montage"
DE102017222639A1 (de) 2017-01-31 2018-08-02 Continental Teves Ag & Co. Ohg Festsattelkraftfahrzeugteilbelagscheibenbremse mit einer Stahlblechbügellüftspielfeder

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996008663A1 (fr) * 1994-09-13 1996-03-21 Kelsey Hayes Company Mecanisme de retrait de machoire pour ensemble frein a disque
JP2000220670A (ja) * 1999-01-29 2000-08-08 Tokico Ltd ディスクブレーキ
US20020043436A1 (en) * 2000-10-18 2002-04-18 Jochen Burgdorf Spot-type disc brake with a spring assembly for a brake lining
US20120085597A1 (en) * 2010-10-08 2012-04-12 Akebono Corporation (North America) Caliper assembly for disc brake system
FR3033012A1 (fr) * 2015-02-25 2016-08-26 Foundation Brakes France "frein a disque comportant au moins un ressort de rappel elastique d'un patin de freinage, ressort de rappel elastique, kit de remplacement et procede de montage"
DE102017222639A1 (de) 2017-01-31 2018-08-02 Continental Teves Ag & Co. Ohg Festsattelkraftfahrzeugteilbelagscheibenbremse mit einer Stahlblechbügellüftspielfeder

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